US5791404A - Flooding reduction on a tubular heat exchanger - Google Patents
Flooding reduction on a tubular heat exchanger Download PDFInfo
- Publication number
- US5791404A US5791404A US08/691,725 US69172596A US5791404A US 5791404 A US5791404 A US 5791404A US 69172596 A US69172596 A US 69172596A US 5791404 A US5791404 A US 5791404A
- Authority
- US
- United States
- Prior art keywords
- tubes
- heat exchanger
- row
- pair
- adjacent
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0012—Recuperative heat exchangers the heat being recuperated from waste water or from condensates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S165/00—Heat exchange
- Y10S165/91—Tube pattern
Definitions
- the invention relates to an improvement in the design and operating performance of pollution removal equipment that also recovers heat from waste gases.
- the invention relates to an improved heat exchanger tube orientation which eliminates flooding in the second stage of an integrated flue gas treatment heat exchanger that can occur when flue gases rising up through the heat exchanger are able to prevent condensate and reagent from falling through the heat exchanger tubes.
- An integrated flue gas treatment condensing heat exchanger is a type of condensing heat exchanger designed to enhance the removal of pollutants from a flue gas stream.
- the integrated flue gas treatment design has two heat exchanger stages instead of one; the interstage transition region connecting the two heat exchanger stages is used to direct the gas to the second heat exchanger as well as act as a collection tank and improve treatment of the gas between stages; the gas flow in the second heat exchanger stage is upward rather than downward; the gas outlet of the second heat exchanger stage is equipped with an alkali reagent spray system; and a mist eliminator is used to separate water formed by condensation and sprays from the flue gas.
- the transition region can be equipped with a water or alkali spray system. This system saturates the flue gas with moisture before it enters the second heat exchanger stage and also assists in removing sulfur pollutants from the gas.
- the second heat exchanger stage is operated in the condensing mode, removing latent heat from the gas along with pollutants.
- the upper region of the second heat exchanger stage is equipped with an alkali solution spray system.
- the gases in this stage flow upward while condensed water droplets and alkali spray fall downward.
- This counter-current gas and droplet flow provides a scrubbing mechanism that enhances particulate and pollutant collection and removal.
- the condensed gases, particulate and reacted alkali solution are all collected at the bottom of the transition section.
- the flue gas outlet of the integrated flue gas treatment system is also equipped with a mist eliminator to reduce the chance of moisture carry over.
- Known heat exchangers have multiple rows of heat exchanging tubes arranged in uniformly spaced staggered arrays, referred to as a triangular pitch, as shown in FIG. 1.
- the gases and condensate flow through the spaces between the tubes created by the staggered spacing.
- the spacing between adjacent heat exchanging tubes is symmetrical and constant, as is the vertical spacing or pitch between tubes in adjacent rows.
- the flue gas travels in an upward direction while the alkali reagent falls downward over the heat exchanger tubes.
- a condition called flooding occurs when the velocity of the flue gas traveling upward through the second stage heat exchanger is sufficient to prevent the downward flow of reagent and condensate between the heat exchanger tubes.
- flooding occurs, the downward force of gravity exerted on the liquid is overcome by the drag force exerted by the upwardly flowing gas. Since the tube spacing is uniform, the velocity between the tubes in the heat exchanger is also highly uniform. Thus, the flooding condition occurs uniformly over the entire cross-section of the heat exchanger.
- the flooding condition is typified by a sudden and large increase in the gas pressure drop through the heat exchanger as liquid is prevented from draining through the heat exchanger.
- Equipment limitations fans, for example
- effectively prevent operation in the flooded condition thus limiting the range of gas flow and reagent flow through a unit.
- flooding can be avoided only by increasing the unrestricted flow area (size) of the heat exchanger so that the critical flow for flooding is not achieved in operation. This is normally achieved by increasing the physical size of the heat exchanger.
- An object of the invention is to overcome many of the limitations imposed by a flooding condition by either increasing the velocity at which flooding occurs or eliminating the sudden large increase in gas phase pressure drop that accompanies the onset of flooding.
- a second stage heat exchanger for an integrated flue gas treatment system having a modified tube geometry configuration which improves the gas flow and condensate counter-flow between the tubes.
- An asymmetrical, or non-uniform, tube arrangement is provided in which some of the tubes in each staggered row of a heat exchanger are selectively spaced or removed to create a greater space between adjacent tubes, and to create non-uniformity in the gas path flow area, without drastically reducing the efficiency of the heat exchanger.
- a non-uniform velocity profile with at least one low velocity region in each row is created, allowing reagent and condensate to drain downward at said low velocity region through the heat exchanger.
- This configuration of heat exchanger tubes can increase the allowable flue gas flow rate and reduces or eliminates the sudden increase in gas phase pressure drop associated with (caused by) the onset of flooding.
- one of every six tubes in an existing heat exchanger would be removed and in a second embodiment, one of every four tubes is eliminated, providing multiple channels or drains through the array of heat exchanging tubes in the heat exchanger.
- FIG. 1 is a front sectional elevation of an array of heat exchanging tubes as known in the art
- FIG. 2 is a front sectional elevation of an array of heat exchanging tubes according to a first embodiment of the invention wherein one out of every six tubes has been removed from the array;
- FIG. 3 is a front sectional elevation of an array of heat exchanging tubes according to a second embodiment of the invention one out of every four tubes has been removed from the array;
- FIG. 4 is a graph plotting the relationship of volumetric flow through the heat exchanger against the observed pressure drop across the heat exchanger for each of the heat exchange arrangements shown in FIGS. 1-3 at a specific reagent spray liquid flux;
- FIG. 5 is a graph plotting the volumetric flow through a second stage heat exchanger against the observed pressure drop across the heat exchanger for each of the three heat exchanging tube arrangements as shown in FIGS. 1-3 with greater reagent spray liquid flux than shown in FIG. 4.
- FIG. 1 shows a heat exchanger 50 with a conventional array 15 of heat exchanger tubes 10 with a uniform triangular pitch.
- a standard geometry tube array of the heat exchanger tubes 10 there is a limited gap between adjacent tubes for condensate and flue gases to flow between the tubes. Additionally, the gap between the tubes is uniform throughout the tube array 15. In this arrangement, condensate and reagent falling between the tubes must impinge on at least one heat exchanging tube 10 and is likely to impinge multiple tubes 10.
- FIG. 2 shows an embodiment of a heat exchanger 50 in which one out of every six tubes 10 has been removed from the horizontal rows of heat exchanger tubes.
- FIGS. 2 and 3 it will be noted that only a portion of an array of heat exchanger tubes 10 is shown. Other tubes form the balance of each of the staggered, horizontal rows, and the removal of particular tubes shown in the Figs. assumes the presence of such other tubes were taken into account. Actual heat exchangers can have over 100 to 150 or more tubes in each of the staggered rows. Accordingly, the drawing of FIG. 2 merely shows such a portion; a 6 row by 6 column array 20 of tubes 10. In a larger array, the removal of tubes ratio would be maintained accordingly.
- At least one distinct channel 25 is provided between tubes 10 in each horizontal row of tubes in array 20.
- a conventional array 15 has a center to center tube separation of 1.75 inches.
- at least one adjacent pair of tubes 10 has a center to center distance that is twice as large as the distance between the remaining pairs of adjacent tubes 10, or in the case of a standard separation, 3.5 inches.
- the increased separation distance between tubes 10 creates a non-uniform cross-sectional flow area, which results in a non-uniform gas velocity profile.
- the pattern would repeat as required to provide multiple channels 25 across the entire width of the heat exchanger 50.
- the non-uniform gas velocity profile provides regions of low gas velocity that allows the drainage of condensate and alkali spray downward through the heat exchanger. This occurs even though flooding would be predicted based on the average gas velocity.
- FIG. 3 shows an array 30 in which one of every four tubes 10 has been removed from the rows of the array 30, to provide the multiple channels 25 in each row of tubes.
- This orientation or arrangement of tubes 10 further improves the counter-flow characteristics of flue gases and condensate material through the heat exchanger 50.
- FIGS. 4 and 5 graphically show the results of operating the second stage heat exchanger of an integrated gas flue gas treatment system using each of the three tube arrangements in FIGS. 1-3 at two different reagent spray flow rates.
- curves A conventional symmetric triangular pitch tube array, 1.0 gpm/ft 2 liquid flux
- D conventional symmetric triangular pitch tube array, 2.0 gpm/ft 2 liquid flux
- the non-uniform tube geometry configuration reduces or eliminates the sudden, large increase in pressure drop associated with flooding in the heat exchanger. This allows continuous operation of the unit without the reagent spray or condensed water becoming suspended in the heat exchanger flue gas flow.
- Additional performance improvements that are realized using an asymmetrical, or non-uniform tube configuration design for the second stage heat exchanger of an integrated flue gas treatment design includes allowing a unit to operate at optimal design conditions wherein gas and reagent flow are optimized for maximum heat recovery and pollutant removal, without encountering large pressure drops across the second stage heat exchanger due to flooding. In the flooded condition, energy consumption of the integrated flue gas treatment is increased because of the pressure drop caused by the suspension of liquid in the second stage heat exchanger.
- the asymmetrical, or non-uniform, tube arrangement designs allows the unit to be operated over a wider range of gas and liquid flow ranges, thus increasing the number of potential applications.
- the reagent liquid flux required to achieve the required pollutant removal will also vary with the activity of the reagent. For example, using a sodium reagent, the integrated flue gas treatment system can achieve greater than 90% SO 2 recovery with a liquid flux of about 6 gpm/ft 2 . If a less reactive reagent is used, a higher liquid flux will be required to achieve the same SO 2 removal efficiency.
- Reagents that are less expensive and more environmentally acceptable can be considered if the unit can be operated efficiently at higher reagent flow rates. As shown in the graphs of FIGS. 4 and 5, higher reagent flow rates can be successfully used with the asymmetrical tube arrays 20 and 30 and still exhibit improved functionality at higher volumetric flow rates. Further, when flooding occurs, reagent and condensate accumulate at the top of the second stage heat exchanger and overload the mist eliminators. This allows reagent, pollutants and condensate to pass downstream of the integrated flue gas treatment system and possibly into the atmosphere. By reducing or eliminating flooding conditions, the asymmetric tube arrays 20 and 30 help to prevent this problem.
- Non-uniform tube arrays 20 and 30 does not have a large detrimental effect on the heat recovery performance of an integrated flue gas treatment system.
- Heat recovery occurs throughout the integrated flue gas treatment system and in one common embodiment, about 60% of the usable heat is recovered in the first heat exchanger stage, leaving only 40% of the recovery burden to the second heat exchanger state. Therefore, if one in four tubes is removed from the second heat exchanger stage as in array 30, there will be a 25% reduction in heat transfer surface in the heat exchanger stage but only a 10% reduction in the ability of the integrated flue gas treatment to recover usable heat.
- the effect on pollution removal performance is also minimal for the asymmetric tube arrays 20, 30.
- the amount of pollutants removed from the gas is a function of reagent surface area due to reagent spray and the surface area of the tubes 10. If the embodiment of array 30 is used, the SO 2 removal efficiency decreases only from about 92% to about 87% pollutant removal. However, because of the reduction or elimination of flooding conditions during operation, if additional pollutant removal is needed, the reagent liquid flux can be increased to obtain the desired value.
- heat exchanger tube arrays in which one in four and one in six tubes are eliminated have been described, other ratios, such as one in three, one in five, one in n (where n is an integer greater than 1, i.e., 2, 3, 4, . . . n, but of course, less than the number of tubes in a given row) may be used as well, as long as the overall spacing between tubes in a given horizontal row is asymmetric, or non-uniform.
- the locations where the resulting asymmetric, or non-uniform spacings are provided in any given row are not located near similar non-uniform spacings of an adjacent upper or lower row, so that a continuous, substantially, vertical zig-zag lane is not provided throughout the array of heat exchanger tubes.
- the arrangement of tubes according to the present invention would still prevent flooding, and still perform its heat exchanging and pollutant-removal functions, albeit perhaps at less than maximum efficiency.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Treating Waste Gases (AREA)
Abstract
Description
Claims (17)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/691,725 US5791404A (en) | 1996-08-02 | 1996-08-02 | Flooding reduction on a tubular heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/691,725 US5791404A (en) | 1996-08-02 | 1996-08-02 | Flooding reduction on a tubular heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US5791404A true US5791404A (en) | 1998-08-11 |
Family
ID=24777701
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/691,725 Expired - Lifetime US5791404A (en) | 1996-08-02 | 1996-08-02 | Flooding reduction on a tubular heat exchanger |
Country Status (1)
Country | Link |
---|---|
US (1) | US5791404A (en) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050144966A1 (en) * | 2002-04-30 | 2005-07-07 | Carrier Commercial Refrigeration, Inc. | Refrigerated merchandiser with foul-resistant condenser |
US6966200B2 (en) * | 2000-04-26 | 2005-11-22 | Mitsubishi Heavy Industries, Ltd. | Evaporator and refrigerator |
US20050257922A1 (en) * | 2004-05-19 | 2005-11-24 | Shabtay Yoram L | High pressure high temperature charge air cooler |
US20060080998A1 (en) * | 2004-10-13 | 2006-04-20 | Paul De Larminat | Falling film evaporator |
US20080216995A1 (en) * | 2007-03-07 | 2008-09-11 | Abb Oy | Arrangement in a heat exchanger |
US20090178790A1 (en) * | 2008-01-11 | 2009-07-16 | Johnson Controls Technology Company | Vapor compression system |
WO2010017853A1 (en) * | 2008-08-12 | 2010-02-18 | Gea Air Treatment Gmbh | Pipe bundle heat exchanger with variably selected pipe spacing |
CN101943540A (en) * | 2009-07-06 | 2011-01-12 | 巴伯考克博斯格服务股份有限公司 | The tubular type adjuster that is used for indirect heat exchange |
US20110056664A1 (en) * | 2009-09-08 | 2011-03-10 | Johnson Controls Technology Company | Vapor compression system |
US20110120181A1 (en) * | 2006-12-21 | 2011-05-26 | Johnson Controls Technology Company | Falling film evaporator |
US10006662B2 (en) | 2013-01-21 | 2018-06-26 | Carrier Corporation | Condensing heat exchanger fins with enhanced airflow |
CN109237977A (en) * | 2017-07-10 | 2019-01-18 | 美的集团股份有限公司 | heat exchange module and heat exchanger |
US10209013B2 (en) | 2010-09-03 | 2019-02-19 | Johnson Controls Technology Company | Vapor compression system |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1577477A (en) * | 1923-05-17 | 1926-03-23 | Sue R Mallory | Engine-cooling system |
US2411097A (en) * | 1944-03-16 | 1946-11-12 | American Locomotive Co | Heat exchanger |
US3180408A (en) * | 1961-06-23 | 1965-04-27 | Braun & Co C F | Heat exchanger apparatus |
US3326280A (en) * | 1962-11-22 | 1967-06-20 | Air Liquide | Heat exchanger with baffle structure |
JPS5949495A (en) * | 1982-09-13 | 1984-03-22 | Babcock Hitachi Kk | Heat exchanger |
JPS62194189A (en) * | 1986-02-19 | 1987-08-26 | Hitachi Ltd | Rankine medium evaporator |
JPH036388A (en) * | 1989-06-01 | 1991-01-11 | Naramoto Rika Kogyo Kk | Method for activating deteriorated waste alkaline degreasing solution or alkaline electrolytic degreasing solution |
US5113928A (en) * | 1989-07-10 | 1992-05-19 | Thermal Transfer Products, Ltd. | Heat exchanger with fluid pressure relief means |
-
1996
- 1996-08-02 US US08/691,725 patent/US5791404A/en not_active Expired - Lifetime
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1577477A (en) * | 1923-05-17 | 1926-03-23 | Sue R Mallory | Engine-cooling system |
US2411097A (en) * | 1944-03-16 | 1946-11-12 | American Locomotive Co | Heat exchanger |
US3180408A (en) * | 1961-06-23 | 1965-04-27 | Braun & Co C F | Heat exchanger apparatus |
US3326280A (en) * | 1962-11-22 | 1967-06-20 | Air Liquide | Heat exchanger with baffle structure |
JPS5949495A (en) * | 1982-09-13 | 1984-03-22 | Babcock Hitachi Kk | Heat exchanger |
JPS62194189A (en) * | 1986-02-19 | 1987-08-26 | Hitachi Ltd | Rankine medium evaporator |
JPH036388A (en) * | 1989-06-01 | 1991-01-11 | Naramoto Rika Kogyo Kk | Method for activating deteriorated waste alkaline degreasing solution or alkaline electrolytic degreasing solution |
US5113928A (en) * | 1989-07-10 | 1992-05-19 | Thermal Transfer Products, Ltd. | Heat exchanger with fluid pressure relief means |
Cited By (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6966200B2 (en) * | 2000-04-26 | 2005-11-22 | Mitsubishi Heavy Industries, Ltd. | Evaporator and refrigerator |
US20050150241A1 (en) * | 2002-04-30 | 2005-07-14 | Carrier Commercial Refrigeration, Inc. | Refrigerated merchandiser with foul-resistant condenser |
US7028497B2 (en) * | 2002-04-30 | 2006-04-18 | Carrier Commercial Refrigeration, Inc. | Refrigerated merchandiser with foul-resistant condenser |
US7065977B2 (en) * | 2002-04-30 | 2006-06-27 | Carrier Commercial Refrigeration, Inc. | Refrigerated merchandiser with foul-resistant condenser |
US20050144966A1 (en) * | 2002-04-30 | 2005-07-07 | Carrier Commercial Refrigeration, Inc. | Refrigerated merchandiser with foul-resistant condenser |
US20050257922A1 (en) * | 2004-05-19 | 2005-11-24 | Shabtay Yoram L | High pressure high temperature charge air cooler |
US6997248B2 (en) * | 2004-05-19 | 2006-02-14 | Outokumpu Oyj | High pressure high temperature charge air cooler |
US7849710B2 (en) | 2004-10-13 | 2010-12-14 | York International Corporation | Falling film evaporator |
US20060080998A1 (en) * | 2004-10-13 | 2006-04-20 | Paul De Larminat | Falling film evaporator |
US8650905B2 (en) | 2006-12-21 | 2014-02-18 | Johnson Controls Technology Company | Falling film evaporator |
US20110120181A1 (en) * | 2006-12-21 | 2011-05-26 | Johnson Controls Technology Company | Falling film evaporator |
US20080216995A1 (en) * | 2007-03-07 | 2008-09-11 | Abb Oy | Arrangement in a heat exchanger |
US20090178790A1 (en) * | 2008-01-11 | 2009-07-16 | Johnson Controls Technology Company | Vapor compression system |
US20100276130A1 (en) * | 2008-01-11 | 2010-11-04 | Johnson Controls Technology Company | Heat exchanger |
US20100319395A1 (en) * | 2008-01-11 | 2010-12-23 | Johnson Controls Technology Company | Heat exchanger |
US20100326108A1 (en) * | 2008-01-11 | 2010-12-30 | Johnson Controls Technology Company | Vapor compression system |
US20100242533A1 (en) * | 2008-01-11 | 2010-09-30 | Johnson Controls Technology Company | Heat exchanger |
US10317117B2 (en) | 2008-01-11 | 2019-06-11 | Johnson Controls Technology Company | Vapor compression system |
US9347715B2 (en) | 2008-01-11 | 2016-05-24 | Johnson Controls Technology Company | Vapor compression system |
US8863551B2 (en) | 2008-01-11 | 2014-10-21 | Johnson Controls Technology Company | Heat exchanger |
US8302426B2 (en) | 2008-01-11 | 2012-11-06 | Johnson Controls Technology Company | Heat exchanger |
DE102008038658A1 (en) * | 2008-08-12 | 2010-02-18 | Gea Air Treatment Gmbh | Tube heat exchanger |
WO2010017853A1 (en) * | 2008-08-12 | 2010-02-18 | Gea Air Treatment Gmbh | Pipe bundle heat exchanger with variably selected pipe spacing |
CN101943540A (en) * | 2009-07-06 | 2011-01-12 | 巴伯考克博斯格服务股份有限公司 | The tubular type adjuster that is used for indirect heat exchange |
CN101943540B (en) * | 2009-07-06 | 2013-07-10 | 巴伯考克博斯格服务股份有限公司 | Tube register for indirect heat exchange |
WO2011003717A3 (en) * | 2009-07-06 | 2011-07-07 | Babcock Borsig Service Gmbh | Tube register for indirect heat exchange |
US10048012B2 (en) | 2009-07-06 | 2018-08-14 | Babcock Borsig Service Gmbh | Tube register for indirect heat exchange |
DE102009031969A1 (en) * | 2009-07-06 | 2011-01-13 | Babcock Borsig Service Gmbh | Pipe register for indirect heat exchange |
US20110056664A1 (en) * | 2009-09-08 | 2011-03-10 | Johnson Controls Technology Company | Vapor compression system |
US10209013B2 (en) | 2010-09-03 | 2019-02-19 | Johnson Controls Technology Company | Vapor compression system |
US10006662B2 (en) | 2013-01-21 | 2018-06-26 | Carrier Corporation | Condensing heat exchanger fins with enhanced airflow |
CN109237977A (en) * | 2017-07-10 | 2019-01-18 | 美的集团股份有限公司 | heat exchange module and heat exchanger |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5791404A (en) | Flooding reduction on a tubular heat exchanger | |
CA2446171C (en) | Flue gas desulfurization system with a stepped tray | |
US4269812A (en) | Horizontal cross-flow scrubber for sulfur oxide removal | |
US4732585A (en) | Fluid treating for removal of components or for transfer of heat, momentum-apparatus and method | |
USRE33444E (en) | Fluid treating for removal of components or for transfer of heat, momentum-apparatus and method | |
CA2192207C (en) | Chevron-type mist eliminator and system | |
US4601731A (en) | Chevron-type mist eliminator and method | |
US4514202A (en) | Air stream entrained water eliminator for cross flow cooling tower | |
RU2000104515A (en) | Fluid distribution system | |
WO1988007166A1 (en) | Gas liquid tower structure | |
US6036756A (en) | Retrofit of a center inlet type scrubber with absorption/gas distribution tray to improve gas-liquid contact in the absorption zone | |
US4230179A (en) | Plate type condensers | |
RU2416461C1 (en) | Package vortex nozzle for heat-and-mass exchange column apparatuses | |
US6287367B1 (en) | High-capacity vapor/liquid contacting device | |
US4028077A (en) | Mist eliminator | |
JPH0979769A (en) | Heat exchanger with brazing plate and treating method of fluid of two phase in heat exchanger thereof | |
US20080257162A1 (en) | Efficient drop separator | |
US4511379A (en) | Apparatus for treating flue gas and methanol containing effluents | |
US6488899B1 (en) | Low pressure drop inlet design to promote good gas flow patterns in high velocity absorbers | |
CN205392080U (en) | A separator for absorption tower | |
JPH09141048A (en) | Wet flue gas desulfurizing method and device therefor | |
CN109481992A (en) | A kind of water collection type dedusting demister and system | |
EP0149307B1 (en) | Fluid treating | |
JPH119956A (en) | Absorption tower of wet flue gas desulfurizer | |
GB1559329A (en) | Air cooled atmospheric heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: BABCOCK & WILCOX COMPANY, THE, LOUISIANA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BAILEY, RALPH T.;SCHULZE, KARL H.;JOHNSON, DENNIS W.;AND OTHERS;REEL/FRAME:008299/0951;SIGNING DATES FROM 19960930 TO 19961009 |
|
AS | Assignment |
Owner name: MCDERMOTT TECHNOLOGY, INC., LOUISIANA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BABCOCK & WILCOX COMPANY, THE;REEL/FRAME:008820/0595 Effective date: 19970630 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
AS | Assignment |
Owner name: MCDERMOTT TECHNOLOGY, INC., LOUISIANA Free format text: CORRECT ASSIGNMENT AS ORIGINALLY RECORDED ON REEL 8820 FRAME 0595 TO DELETE ITEMS ON ATTACHED PAGE 2.;ASSIGNOR:BABCOCK & WILCOX COMPANY, THE;REEL/FRAME:009405/0374 Effective date: 19970630 |
|
FEPP | Fee payment procedure |
Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
REMI | Maintenance fee reminder mailed | ||
FPAY | Fee payment |
Year of fee payment: 8 |
|
AS | Assignment |
Owner name: THE BABCOCK & WILCOX COMPANY, OHIO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MCDERMOTT TECHNOLOGY, INC.;REEL/FRAME:017186/0749 Effective date: 20060221 |
|
AS | Assignment |
Owner name: CREDIT SUISSE, CAYMAN ISLANDS BRANCH, AS COLLATERA Free format text: SECURITY AGREEMENT;ASSIGNOR:THE BABCOCK & WILCOX COMPANY;REEL/FRAME:017344/0565 Effective date: 20060222 |
|
AS | Assignment |
Owner name: THE BABCOCK & WILCOX POWER GENERATION GROUP, INC., Free format text: CHANGE OF NAME;ASSIGNOR:THE BABCOCK & WILCOX COMPANY;REEL/FRAME:021998/0870 Effective date: 20071120 |
|
FPAY | Fee payment |
Year of fee payment: 12 |
|
AS | Assignment |
Owner name: BABCOCK & WILCOX EBENSBURG POWER, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: DIAMOND OPERATING CO., INC., PENNSYLVANIA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: AMERICON, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: REVLOC RECLAMATION SERVICE, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX CHINA HOLDINGS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX CONSTRUCTION CO., INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: B & W SERVICE COMPANY, NORTH CAROLINA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: APPLIED SYNERGISTICS, INC., VIRGINIA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: DIAMOND POWER AUSTRALIA HOLDINGS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: PALM BEACH RESOURCE RECOVERY CORPORATION, FLORIDA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: AMERICON EQUIPMENT SERVICES, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: THE BABCOCK & WILCOX COMPANY, NORTH CAROLINA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX DENMARK HOLDINGS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: NORTH COUNTY RECYCLING, INC., NORTH CAROLINA Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: POWER SYSTEMS OPERATIONS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: DIAMOND POWER EQUITY INVESTMENTS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: DIAMOND POWER INTERNATIONAL, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: NATIONAL ECOLOGY COMPANY, OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: DIAMOND POWER CHINA HOLDINGS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX EQUITY INVESTMENTS, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX INTERNATIONAL SALES AND SERVICE C Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 Owner name: BABCOCK & WILCOX INTERNATIONAL, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CREDIT SUISSE AG, CAYMAN ISLANDS BRANCH;REEL/FRAME:024776/0693 Effective date: 20100503 |
|
AS | Assignment |
Owner name: BANK OF AMERICA, N.A., AS ADMINISTRATIVE AGENT, CA Free format text: NOTICE OF GRANT OF SECURITY INTEREST IN PATENTS;ASSIGNOR:BABCOCK & WILCOX POWER GENERATION GROUP, INC. (F.K.A. THE BABCOCK & WILCOX COMPANY);REEL/FRAME:025066/0080 Effective date: 20100503 |
|
AS | Assignment |
Owner name: BANK OF AMERICA, N.A., AS ADMINISTRATIVE AGENT, CA Free format text: SECURITY INTEREST;ASSIGNOR:BABCOCK & WILCOX POWER GENERATION GROUP, INC.;REEL/FRAME:033380/0744 Effective date: 20140624 |
|
AS | Assignment |
Owner name: BABCOCK & WILCOX POWER GENERATION GROUP, INC., OHI Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE NAME PREVIOUSLY RECORDED AT REEL: 021998 FRAME: 0870. ASSIGNOR(S) HEREBY CONFIRMS THE CHANGE OF NAME;ASSIGNOR:THE BABCOCK & WILCOX COMPANY;REEL/FRAME:035871/0019 Effective date: 20071120 |
|
AS | Assignment |
Owner name: BANK OF AMERICA, N.A., AS ADMINISTRATIVE AGENT, CA Free format text: SECURITY INTEREST;ASSIGNOR:BABCOCK & WILCOX POWER GENERATION GROUP, INC. (TO BE RENAMED THE BABCOCK AND WILCOX COMPANY);REEL/FRAME:036201/0598 Effective date: 20150630 |
|
AS | Assignment |
Owner name: THE BABCOCK & WILCOX COMPANY, OHIO Free format text: CHANGE OF NAME;ASSIGNOR:BABCOCK & WILCOX POWER GENERATION GROUP, INC.;REEL/FRAME:036675/0434 Effective date: 20150630 |
|
AS | Assignment |
Owner name: BABCOCK & WILCOX MEGTEC, LLC, WISCONSIN Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: SOFCO-EFS HOLDINGS LLC, OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: BABCOCK & WILCOX TECHNOLOGY, LLC (F/K/A MCDERMOTT TECHNOLOGY, INC.), OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: BABCOCK & WILCOX SPIG, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: THE BABCOCK & WILCOX COMPANY (F/K/A BABCOCK & WILCOX POWER GENERATION GROUP, INC.), OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: MEGTEC TURBOSONIC TECHNOLOGIES, INC., ONTARIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 Owner name: DIAMOND POWER INTERNATIONAL, LLC (F/K/A DIAMOND POWER INTERNATIONAL, INC.), OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA, N.A.;REEL/FRAME:057337/0823 Effective date: 20210630 |